JP2006177446A - Tapered roller bearing with aligning ring - Google Patents

Tapered roller bearing with aligning ring Download PDF

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Publication number
JP2006177446A
JP2006177446A JP2004371363A JP2004371363A JP2006177446A JP 2006177446 A JP2006177446 A JP 2006177446A JP 2004371363 A JP2004371363 A JP 2004371363A JP 2004371363 A JP2004371363 A JP 2004371363A JP 2006177446 A JP2006177446 A JP 2006177446A
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Prior art keywords
roller bearing
tapered roller
double row
bearing
double
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JP2004371363A
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Inventor
Makoto Serio
誠 芹生
Naoki Nakagawa
直樹 中川
Junichi Hattori
純一 服部
Naoki Matsumori
直樹 松森
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/084—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface sliding on a complementary spherical surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double-row tapered roller bearing having an aligning property as maintaining high axial load bearing capability for properly supporting an operating load different between right and left rows, depending on the status of the load in each row. <P>SOLUTION: The double-row tapered roller bearing 11 comprises an inner ring 12, an outer ring 13 having a convex spherical outer diameter face, and tapered rollers 14, 15 different in roller lengths arranged in right and left rows between the inner ring 12 and the outer ring 13. Further outside the outer ring 13, an aligning ring 17 is provided which has a concave spherical inner diameter face for receiving the outer diameter face of the outer ring 13. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は、複列円錐ころ軸受に関し、特に左右の列の円錐ころに不均等な荷重が作用し、かつ、調心性が必要とされる複列円錐ころ軸受およびそのような軸受を備えた風力発電機の主軸支持構造に関するものである。   The present invention relates to a double-row tapered roller bearing, and more particularly, a double-row tapered roller bearing in which uneven loads are applied to left and right rows of tapered rollers and alignment is required, and a wind turbine including such a bearing. The present invention relates to a main shaft support structure of a generator.

風力発電機の主軸を回転自在に支持するのに好適な軸受として、自動調心ころ軸受が、例えば特開２００４−１１７３７号公報（特許文献１）に開示されている。同公報に開示されているように、大型の風力発電機における主軸用軸受には、図１に示すような大型の複列自動調心ころ軸受１が用いられることが多い。   As a bearing suitable for rotatably supporting the main shaft of a wind power generator, a self-aligning roller bearing is disclosed in, for example, Japanese Patent Application Laid-Open No. 2004-11737 (Patent Document 1). As disclosed in the publication, a large double row self-aligning roller bearing 1 as shown in FIG. 1 is often used for a main shaft bearing in a large wind power generator.

風力発電機の風車の主軸２は、ブレード３が設けられた先端側を片持ち支持するようにハウジング４に取り付けられているので、その片持ち支持用の軸受として、通常、主軸２の撓みに対して調心性を有する大型の自動調心ころ軸受１が使用される。自動調心ころ軸受１は、内輪５と、外輪６と、複列の球面ころ７，８とを備える。   Since the main shaft 2 of the wind turbine of the wind power generator is attached to the housing 4 so as to cantilever-support the tip side where the blade 3 is provided, the main shaft 2 is usually used as a bearing for supporting the cantilever. On the other hand, a large self-aligning roller bearing 1 having alignment is used. The self-aligning roller bearing 1 includes an inner ring 5, an outer ring 6, and double-row spherical rollers 7 and 8.

上記の風力発電機の主軸支持用の複列自動調心ころ軸受１には、風車の回転中はラジアル荷重の他に大きなアキシアル荷重が負荷される。この場合、複列の球面ころ７，８のうち、ブレード３から遠いほうの列の球面ころ８が、ラジアル荷重とアキシアル荷重とを同時に受けることになる。一方、ブレード３に近い方の列の球面ころ７については、アキシアル荷重があまりかからず、専らラジアル荷重を受けることになる。
特開２００４−１１７３７号公報（段落番号０００２等） The double row spherical roller bearing 1 for supporting the main shaft of the wind power generator is loaded with a large axial load in addition to the radial load during rotation of the wind turbine. In this case, the spherical roller 8 in the row farther from the blade 3 out of the double row spherical rollers 7 and 8 receives the radial load and the axial load at the same time. On the other hand, the spherical roller 7 in the row closer to the blade 3 is not subjected to much axial load and is exclusively subjected to radial load.
JP 2004-11737 A (paragraph number 0002 etc.)

上記の複列自動調心ころ軸受１は、アキシアル荷重負荷能力があまり高くないので、ブレード３から遠い球面ころ８に十分な負荷容量を確保するためには軸受の大型化が必要となる。しかし、大型化した場合には、ブレード３に近い球面ころ７は軽負荷となり、球面ころ７が内輪５および外輪６の軌道面５ａ，６ａですべりを生じ、表面損傷や磨耗を生じるという問題がある。   Since the double-row self-aligning roller bearing 1 does not have a high axial load capacity, it is necessary to increase the size of the bearing in order to ensure a sufficient load capacity for the spherical roller 8 far from the blade 3. However, when the size is increased, the spherical roller 7 close to the blade 3 is lightly loaded, and the spherical roller 7 slips on the raceway surfaces 5a and 6a of the inner ring 5 and the outer ring 6 to cause surface damage and wear. is there.

そこで、風力発電機の主軸支持用の軸受として、複列自動調心ころ軸受に代えて、アキシアル荷重負荷能力の高い複列円錐ころ軸受を用いることが考えられる。これにより、軸受を大型化することなく、十分な負荷容量を確保することが可能となる。   Therefore, it is conceivable to use a double-row tapered roller bearing having a high axial load-loading capacity instead of the double-row self-aligning roller bearing as a bearing for supporting the main shaft of the wind power generator. This makes it possible to ensure a sufficient load capacity without increasing the size of the bearing.

ただし、複列円錐ころ軸受は、一般に調心性を有していないので、主軸が撓むことによりエッジ応力が大きくなるという問題が生じる。また、左右の列で異なる荷重が作用する環境で、各列の負荷状況に応じた適切な支持を行う必要もある。   However, since the double-row tapered roller bearing is generally not self-aligning, there is a problem that the edge stress increases due to the bending of the main shaft. In addition, in an environment where different loads act on the left and right rows, it is necessary to provide appropriate support according to the load status of each row.

本発明の目的は、複列円錐ころ軸受の高いアキシアル荷重負荷能力を維持したまま、調心性を有し、かつ、左右の列で異なる荷重が作用する環境で、各列の負荷状況に応じた適正な支持を行うことができる複列円錐ころ軸受を提供することである。   The object of the present invention is to maintain the high axial load load capacity of the double row tapered roller bearing, have alignment and respond to the load situation of each row in an environment where different loads act on the left and right rows. To provide a double row tapered roller bearing capable of providing proper support.

この発明に係る複列円錐ころ軸受は、内輪と、凸状球面の外径面を有する外輪と、内輪および外輪の間に複列に配置され、左右の列で負荷容量が互いに異なる複数の円錐ころと、外輪の外径面を受け入れる凹状球面の内径面を有する調心リングとを備える。   A double-row tapered roller bearing according to the present invention includes a plurality of cones arranged in a double row between an inner ring, an outer ring having a convex spherical outer diameter surface, and an inner ring and an outer ring and having different load capacities in the left and right rows. A roller and a centering ring having a concave spherical inner diameter surface that receives the outer diameter surface of the outer ring.

上記の構成の複列円錐ころ軸受は、外輪に調心リングを備えることにより、回転軸の撓み等による芯ずれに対して自動調心性を有する。   The double-row tapered roller bearing having the above-described configuration has a self-aligning property with respect to misalignment due to the deflection of the rotating shaft or the like by providing a centering ring on the outer ring.

好ましくは、複数の円錐ころは、左右の列でころ長さが互いに異なるとよい。これにより、ころ長さの長い円錐ころを有する列の負荷容量を高くすることができる。   Preferably, the plurality of tapered rollers may have different roller lengths in the left and right rows. Thereby, the load capacity of the row | line | column which has a tapered roller with a long roller length can be made high.

好ましくは、複数の円錐ころは、左右の列でころ径が互いに異なるとよい。これにより、ころ径の大きい円錐ころを有する列の負荷容量を高くすることができる。   Preferably, the plurality of tapered rollers may have different roller diameters in the left and right rows. Thereby, the load capacity of the row | line | column which has a tapered roller with a large roller diameter can be made high.

好ましくは、複数の円錐ころは、左右の列で一方を中実ころとし、他方を中空ころとするとよい。これにより、中実ころを使用する列の負荷容量を高くすることができる。また、中空ころの中空部には潤滑油が溜まるので、中空ころの端面の潤滑性能が向上し、潤滑寿命を伸ばすことができる。   Preferably, in the plurality of tapered rollers, one of the left and right rows is a solid roller and the other is a hollow roller. Thereby, the load capacity of the row | line | column which uses a solid roller can be made high. Further, since the lubricating oil accumulates in the hollow portion of the hollow roller, the lubricating performance of the end surface of the hollow roller is improved, and the lubricating life can be extended.

複列円錐ころ軸受は、例えば、左右の列の円錐ころの小径側端部を向かい合わせた背面組み合わせ軸受である。この構成とすることにより、軸受の回転中心線と、左右の列の円錐ころと内外輪の接触線との交点の距離（以下「作用点間距離」という）が長くなるので、ラジアル剛性が向上する。   The double row tapered roller bearing is, for example, a back combination bearing in which the small diameter side ends of the tapered rollers in the left and right rows face each other. With this configuration, the radial distance is improved because the distance between the rotation center line of the bearing and the contact line between the tapered rollers in the left and right rows and the inner and outer rings (hereinafter referred to as “distance between the operating points”) is increased. To do.

複列円錐ころ軸受は、例えば、左右の列の円錐ころの大径側端部を向かい合わせた正面組み合わせ軸受である。この構成とすることにより、外輪の肉厚が円周上であまり差のないバランスの良い設計ができるとともに、同じ断面高さであれば、背面組み合わせ軸受より負荷容量を大きくすることができる。   The double row tapered roller bearing is, for example, a front combination bearing in which the large-diameter side ends of the tapered rollers in the left and right rows face each other. With this configuration, a well-balanced design in which the outer ring wall thickness is not much different on the circumference can be achieved, and the load capacity can be made larger than that of the rear combination bearing if the cross-sectional height is the same.

この発明に係る風力発電機の主軸支持構造は、風力を受けるブレードと、その一端がブレードに固定され、ブレードとともに回転する主軸と、固定部材に組み込まれ、主軸を回転自在に支持する複列円錐ころ軸受とを備える。複列円錐ころ軸受に注目すると、内輪と、凸状球面の外径面を有する外輪と、内輪および外輪の間に複列に配置され、左右の列で負荷容量が互いに異なる複数の円錐ころと、外輪の外径面を受け入れる凹状球面の内径面を有する調心リングとを備えることを特徴とする。   A main shaft support structure of a wind power generator according to the present invention includes a blade that receives wind power, a main shaft that is fixed to the blade and rotated together with the blade, and a double-row cone that is incorporated in a fixed member and rotatably supports the main shaft. A roller bearing. When paying attention to the double row tapered roller bearing, the inner ring, the outer ring having a convex spherical outer diameter surface, and the plurality of tapered rollers arranged in a double row between the inner ring and the outer ring and having different load capacities in the left and right rows And a centering ring having a concave spherical inner diameter surface for receiving the outer diameter surface of the outer ring.

上記構成とすることにより、主軸に作用する特性に応じた適正な支持を行えるので、信頼性が高く、長寿命の主軸支持構造が得られる。   By adopting the above-described configuration, it is possible to perform appropriate support according to the characteristics acting on the main shaft, so that a main shaft support structure with high reliability and long life can be obtained.

複列円錐ころ軸受は、例えば、左右の列の円錐ころの小径側端部を向かい合わせた背面組み合わせ軸受であって、ブレードに近い側の円錐ころの負荷容量を大きくするとよい。この構成とすることにより、軸受の作用点間距離が長くなるので、ラジアル剛性が向上する。その結果、さらに信頼性が高く、長寿命の主軸支持構造が得られる。   The double-row tapered roller bearing is, for example, a rear combination bearing in which the small-diameter side ends of the tapered rollers in the left and right rows face each other, and the load capacity of the tapered roller on the side close to the blade may be increased. With this configuration, the distance between the operating points of the bearing is increased, so that radial rigidity is improved. As a result, a spindle support structure with higher reliability and longer life can be obtained.

複列円錐ころ軸受は、例えば、左右の列の円錐ころの大径側端部を向かい合わせた正面組み合わせ軸受であって、ブレードに遠い側の円錐ころの負荷容量を大きくするとよい。この構成とすることにより、外輪の肉厚が円周上であまり差のないバランスの良い設計ができるとともに、同じ断面高さであれば、背面組み合わせ軸受より負荷容量を大きくすることができる。その結果、さらに信頼性が高く、長寿命の主軸支持構造が得られる。   The double-row tapered roller bearing is, for example, a front combination bearing in which the large-diameter side ends of the left and right tapered rollers face each other, and the load capacity of the tapered roller on the side far from the blade may be increased. With this configuration, a well-balanced design in which the outer ring wall thickness is not much different on the circumference can be achieved, and the load capacity can be made larger than that of the rear combination bearing if the cross-sectional height is the same. As a result, a spindle support structure with higher reliability and longer life can be obtained.

この発明に係る複列円錐ころ軸受は、高いアキシアル荷重負荷能力を維持したまま、調心性を有し、かつ、左右の列で異なる荷重が作用する環境で、各列の負荷状況に応じた適正な支持を行うことができる。   The double-row tapered roller bearing according to the present invention has alignment properties while maintaining high axial load carrying capacity, and is suitable for the load situation of each row in an environment where different loads act on the left and right rows. Support can be made.

図２を参照して、この発明に係る複列円錐ころ軸受１１を説明する。   A double-row tapered roller bearing 11 according to the present invention will be described with reference to FIG.

複列円錐ころ軸受１１は、２つの内輪部材の小径側端部を突き合わせた内輪１２と、凸状球面の外径面を有する外輪１３と、内輪１２および外輪１３の間に左右の列でころ長さが互いに異なる複数の円錐ころ１４，１５が配置されている。円錐ころ１４，１５は、各列に別個に設けられた保持器１６によりその間隔が保持されている。外輪１３のさらに外側には、外輪１３の外径面を受け入れる凹状球面の内径面を有する調心リング１７を有する。   The double-row tapered roller bearing 11 is a roller in the left and right rows between the inner ring 12 in which the small diameter side ends of the two inner ring members are butted, the outer ring 13 having a convex spherical outer diameter surface, and the inner ring 12 and the outer ring 13. A plurality of tapered rollers 14, 15 having different lengths are disposed. The interval between the tapered rollers 14 and 15 is maintained by a cage 16 provided separately in each row. Further on the outer side of the outer ring 13, there is a centering ring 17 having a concave spherical inner diameter surface that receives the outer diameter surface of the outer ring 13.

また、複列円錐ころ軸受１１は、左右の列の円錐ころ１４，１５のそれぞれの小径側端部を向かい合わせた背面組み合わせ軸受である。   The double row tapered roller bearing 11 is a back combination bearing in which the small diameter side ends of the tapered rollers 14 and 15 in the left and right rows face each other.

上記の構成の複列円錐ころ軸受１１は、円錐ころ１４のころ長さを円錐ころ１５のころ長さより長くしたので、ころ長さの長い円錐ころ１４の列ではアキシアル荷重負荷能力が高くなる。   In the double row tapered roller bearing 11 configured as described above, the roller length of the tapered roller 14 is longer than the roller length of the tapered roller 15, so that the axial load-loading capability is increased in the row of tapered rollers 14 having a long roller length.

また、凸状球面の外径面を有する外輪１３と、外輪１３の外径面を受け入れる凹状球面の内径面を有する調心リング１７とを備えることにより、複列円錐ころ軸受１１は、回転軸の撓み等による芯ずれに対して自動調心性を有する。   Further, the double-row tapered roller bearing 11 has a rotating shaft by including an outer ring 13 having a convex spherical outer diameter surface and a centering ring 17 having a concave spherical inner diameter surface that receives the outer diameter surface of the outer ring 13. Self-alignment against misalignment due to bending of

さらに、左右の列の円錐ころ１４，１５を背面組み合わせとすることにより、軸受の作用点間距離Ｄが長くなるので、ラジアル剛性が向上する。   Furthermore, since the distance D between the operating points of the bearing is increased by using the tapered rollers 14 and 15 in the left and right rows as a back surface combination, the radial rigidity is improved.

次に、図３を参照して、この発明の他の実施形態に係る複列円錐ころ軸受２１を説明する。   Next, a double row tapered roller bearing 21 according to another embodiment of the present invention will be described with reference to FIG.

複列円錐ころ軸受２１は、２つの内輪部材の大径側端部を突き合わせた内輪２２と、凸状球面の外径面を有する外輪２３と、左右の列でころ長さが互いに異なる複数の円錐ころ２４，２５と、各列に別個に設けられた保持器２６とを備え、外輪２３のさらに外側には、外輪２３の外径面を受け入れる凹状球面の内径面を有する調心リング２７を有する。また、複列円錐ころ軸受２１は、左右の列の円錐ころ２４，２５のそれぞれの大径側端部を向かい合わせた正面組み合わせ軸受である。   The double-row tapered roller bearing 21 includes a plurality of inner rings 22 each having a large-diameter side end portion of two inner ring members abutted against each other, an outer ring 23 having a convex spherical outer diameter surface, and a plurality of different roller lengths in the left and right rows. Tapered rollers 24 and 25 and cages 26 provided separately in each row are provided, and an aligning ring 27 having a concave spherical inner diameter surface for receiving the outer diameter surface of the outer ring 23 is provided on the outer side of the outer ring 23. Have. The double row tapered roller bearing 21 is a front combination bearing in which the large diameter side ends of the tapered rollers 24 and 25 in the left and right rows face each other.

上記構成とすることにより、外輪２３の肉厚が円周上であまり差のないバランスの良い設計ができるとともに、同じ断面高さであれば、図２に示したような背面組み合わせ軸受より負荷容量を大きくすることができる。   With the above configuration, the outer ring 23 can have a well-balanced design in which the thickness of the outer ring 23 is not much different on the circumference, and the load capacity is higher than that of the rear combination bearing as shown in FIG. Can be increased.

上記の各実施形態に係る複列円錐ころ軸受では、左右の列でころ長さが互いに異なる円錐ころを用いた例を示したが、これに限ることなく、左右の列でころ径が互いに異なる円錐ころを用いてもよいし、左右の列でころ長さおよびころ径の両方が異なる円錐ころを用いてもよい。   In the double row tapered roller bearing according to each of the above-described embodiments, the example in which the tapered rollers having different roller lengths in the left and right rows are used has been described. However, the roller diameters in the left and right rows are different from each other. Tapered rollers may be used, or tapered rollers having different roller lengths and roller diameters in the left and right rows may be used.

また、複列円錐ころ軸受の左右の列のいずれか一方の円錐ころを、図４に示すように、両端面に貫通する貫通孔５１を有する中空ころとし、他方を中実ころとすることにより中実ころを使用する列の負荷容量を大きくすることもできる。   Further, as shown in FIG. 4, one of the left and right rows of the double row tapered roller bearing is a hollow roller having through holes 51 penetrating through both end faces, and the other is a solid roller. It is also possible to increase the load capacity of the row using solid rollers.

上記構成とすることにより、中空ころ５０の貫通孔５１内部に潤滑油が溜まるので、中空ころの両端面５２，５３の潤滑性能が向上し、潤滑寿命を伸ばすことが可能となる。   With the above configuration, the lubricating oil is accumulated in the through hole 51 of the hollow roller 50, so that the lubricating performance of the both end faces 52 and 53 of the hollow roller is improved, and the lubricating life can be extended.

上記の実施形態では、左右の円錐ころのころ長さおよびころ径は同一としてもよいが、これに限ることなく、中実ころのころ長さを中空ころよりも長くしてもよく、また、中実ころのころ径を中空ころよりも大きくしてもよく、さらには、中実ころのころ長さおよびころ径を中空ころより大きくしてもよい。   In the above embodiment, the roller length and the roller diameter of the left and right tapered rollers may be the same, but not limited thereto, the solid roller may be longer than the hollow roller, The roller diameter of the solid roller may be larger than that of the hollow roller, and further, the roller length and roller diameter of the solid roller may be larger than that of the hollow roller.

図５および図６は、図２〜図４に示したような本発明の実施形態に係る複列円錐ころ軸受が適用された風力発電機の主軸支持構造の一例を示している。主軸支持構造の主要部品を支持するナセル３２のケーシング３３は、高い位置で、旋回座軸受３１を介して支持台３０上に水平旋回自在に設置されている。一端にブレード３７を保持する主軸３６は、ナセル３２のケーシング３３内で、軸受ハウジング３４に組み込まれた主軸支持軸受３５を介して回転自在に支持されている。主軸３６の他端は増速機３８に接続され、この増速機３８の出力軸が発電機３９のロータ軸に結合されている。ナセル３２は、旋回用モータ４０により、減速機４１を介して任意の角度に旋回させられる。   5 and 6 show an example of a main shaft support structure of a wind power generator to which the double row tapered roller bearing according to the embodiment of the present invention as shown in FIGS. 2 to 4 is applied. The casing 33 of the nacelle 32 that supports the main components of the spindle support structure is installed on the support base 30 via a swivel bearing 31 at a high position so as to be able to turn horizontally. A main shaft 36 holding a blade 37 at one end is rotatably supported in a casing 33 of the nacelle 32 via a main shaft support bearing 35 incorporated in a bearing housing 34. The other end of the main shaft 36 is connected to a speed increaser 38, and the output shaft of the speed increaser 38 is coupled to the rotor shaft of the generator 39. The nacelle 32 is turned at an arbitrary angle by the turning motor 40 via the speed reducer 41.

図示した実施形態では、主軸支持軸受３５は２個並べて設置されているが、１個であってもよい。この主軸支持軸受３５として、本発明の実施形態に係る背面組み合わせの複列円錐ころ軸受を用いる場合には、ブレード３７に近いほうの列に大きな負荷がかかるので、軸受の左側列にころ長さ若しくはころ径の長い円錐ころ、または中実の円錐ころを用いる。一方、本発明の実施形態に係る正面組み合わせの複列円錐ころ軸受を用いる場合には、ブレード３７から遠いほうの列に大きな負荷がかかるので、軸受の右側列にころ長さ若しくはころ径の大きな円錐ころ、または中実の円錐ころを用いる。   In the illustrated embodiment, two spindle support bearings 35 are installed side by side, but may be one. When the double-row tapered roller bearing of the back combination according to the embodiment of the present invention is used as the main shaft support bearing 35, a large load is applied to the row closer to the blade 37. Alternatively, a tapered roller having a long roller diameter or a solid tapered roller is used. On the other hand, when the double-row tapered roller bearing of the front combination according to the embodiment of the present invention is used, a large load is applied to the row farther from the blade 37, so the roller length or the roller diameter is large in the right side row of the bearing. Use tapered rollers or solid tapered rollers.

以上、図面を参照してこの発明の実施形態を説明したが、この発明は、図示した実施形態のものに限定されない。図示した実施形態に対して、この発明と同一の範囲内において、あるいは均等の範囲内において、種々の修正や変形を加えることが可能である。   As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

この発明は、左右の列に不均等な荷重が付加される環境で使用する複列円錐ころ軸受およびそのような軸受を備えた風力発電機の主軸支持構造に有利に利用される。   The present invention is advantageously used for a double-row tapered roller bearing used in an environment where uneven loads are applied to the left and right rows and a main shaft support structure of a wind power generator having such a bearing.

風力発電機の主軸支持軸受の従来例を示す断面図である。It is sectional drawing which shows the prior art example of the spindle support bearing of a wind power generator. この発明の一実施形態に係る複列円錐ころ軸受であって、左右の列の軸受の背面同士を向かい合わせた状態を示す図である。It is a double row tapered roller bearing which concerns on one Embodiment of this invention, Comprising: It is a figure which shows the state which faced back of the bearing of the right and left row | line | column. この発明の他の実施形態に係る複列円錐ころ軸受であって、左右の列の軸受の正面同士を向かい合わせた状態を示す図である。It is a double row tapered roller bearing which concerns on other embodiment of this invention, Comprising: It is a figure which shows the state which faced the front of the bearing of a right-and-left row | line | column. 本発明に係る複列円錐ころ軸受に使用する円錐ころであって、その両端面に貫通する貫通孔を有する円錐ころを示す図である。It is a figure which shows the tapered roller used for the double row tapered roller bearing which concerns on this invention, Comprising: The tapered roller which has the through-hole penetrated in the both end surfaces. 本発明に係る複列円錐ころ軸受を用いた風力発電機の主軸支持構造の一例を示す図である。It is a figure which shows an example of the spindle support structure of the wind power generator using the double row tapered roller bearing which concerns on this invention. 図４に示した風力発電機の主軸支持構造の図解的側面図である。FIG. 5 is a schematic side view of the main shaft support structure of the wind power generator shown in FIG. 4.

符号の説明Explanation of symbols

１ 複列自動調心ころ軸受、２ 風力発電機主軸、３ ブレード、４ ハウジング、１１，２１ 複列円錐ころ軸受、５，１２，２２ 内輪、５ａ 内輪軌道面、６，１３，２３ 外輪、６ａ 外輪軌道面、７，８ 球面ころ、１４，１５，２４，２５，５０ 円錐ころ、１６，２６ 保持器、１７，２７ 調心リング、３０ 支持台、３１ 旋回座軸受、３２ ナセル、３３ ケーシング、３４ 軸受ハウジング、３５ 主軸支持軸受、３６ 主軸、３７ ブレード、３８ 増速機、３９ 発電機、４０ 旋回用モータ、４１減速機、５１ 貫通孔、５２，５３ 円錐ころ端面。
DESCRIPTION OF SYMBOLS 1 Double row self-aligning roller bearing, 2 Wind generator main shaft, 3 Blades, 4 Housing, 11, 21 Double row tapered roller bearing, 5, 12, 22 Inner ring, 5a Inner ring raceway surface, 6, 13, 23 Outer ring, 6a Outer ring raceway surface, 7, 8 spherical roller, 14, 15, 24, 25, 50 tapered roller, 16, 26 cage, 17, 27 aligning ring, 30 support base, 31 swivel bearing, 32 nacelle, 33 casing, 34 bearing housing, 35 spindle support bearing, 36 spindle, 37 blade, 38 speed increaser, 39 generator, 40 turning motor, 41 speed reducer, 51 through hole, 52, 53 tapered roller end face.

Claims (9)

内輪と、
凸状球面の外径面を有する外輪と、
前記内輪および前記外輪の間に複列に配置され、左右の列で負荷容量が互いに異なる複数の円錐ころと、
前記外輪の外径面を受け入れる凹状球面の内径面を有する調心リングとを備える、複列円錐ころ軸受。 Inner ring,
An outer ring having a convex spherical outer diameter surface;
A plurality of tapered rollers arranged in a double row between the inner ring and the outer ring, and having different load capacities in the left and right rows;
A double-row tapered roller bearing comprising a centering ring having a concave spherical inner diameter surface that receives the outer diameter surface of the outer ring. 前記複数の円錐ころは、左右の列でころ長さが互いに異なる、請求項１に記載の複列円錐ころ軸受。   The double row tapered roller bearing according to claim 1, wherein the plurality of tapered rollers have different roller lengths in left and right rows. 前記複数の円錐ころは、左右の列でころ径が互いに異なる、請求項１または２に記載の複列円錐ころ軸受。   The double row tapered roller bearing according to claim 1 or 2, wherein the plurality of tapered rollers have different roller diameters in the left and right rows. 前記複数の円錐ころは、左右の列で一方を中実ころとし、他方を中空ころとした、請求項１〜３のいずれかに記載の複列円錐ころ軸受。   The double-row tapered roller bearing according to any one of claims 1 to 3, wherein one of the plurality of tapered rollers is a solid roller and the other is a hollow roller in the left and right rows. 前記複列円錐ころ軸受は、左右の列の円錐ころの小径側端部を向かい合わせた背面組み合わせ軸受である、請求項１〜４のいずれかに記載の複列円錐ころ軸受。   The double row tapered roller bearing according to any one of claims 1 to 4, wherein the double row tapered roller bearing is a back combination bearing in which the small diameter side ends of the tapered rollers in the left and right rows face each other. 前記複列円錐ころ軸受は、左右の列の円錐ころの大径側端部を向かい合わせた正面組み合わせ軸受である、請求項１〜４のいずれかに記載の複列円錐ころ軸受。   The double row tapered roller bearing according to any one of claims 1 to 4, wherein the double row tapered roller bearing is a front combination bearing in which the large-diameter side ends of the tapered rollers in the left and right rows face each other. 風力を受けるブレードと、
その一端が前記ブレードに固定され、ブレードとともに回転する主軸と、
固定部材に組み込まれ、前記主軸を回転自在に支持する複列円錐ころ軸受とを備えた風力発電機の主軸支持構造において、
前記複列円錐ころ軸受は、内輪と、凸状球面の外径面を有する外輪と、前記内輪および前記外輪の間に複列に配置され、左右の列で負荷容量が互いに異なる複数の円錐ころと、前記外輪の外径面を受け入れる凹状球面の内径面を有する調心リングとを備えることを特徴とする、風力発電機の主軸支持構造。 A blade that receives wind,
One end of which is fixed to the blade and rotates with the blade;
In the main shaft support structure of a wind power generator, which is incorporated in a fixed member and includes a double row tapered roller bearing that rotatably supports the main shaft,
The double row tapered roller bearing includes an inner ring, an outer ring having a convex spherical outer diameter surface, and a plurality of tapered rollers arranged in a double row between the inner ring and the outer ring and having different load capacities in the left and right rows. And a spindle support structure for a wind power generator, comprising a centering ring having a concave spherical inner diameter surface that receives the outer diameter surface of the outer ring. 前記複列円錐ころ軸受は、左右の列の円錐ころの小径側端部を向かい合わせた背面組み合わせ軸受であって、
前記ブレードに近い側の前記円錐ころの負荷容量を大きくしたことを特徴とする、請求項７に記載の風量発電機の主軸支持構造。 The double row tapered roller bearing is a back combination bearing in which the small diameter side ends of the tapered rollers in the left and right rows face each other,
The main shaft support structure for an air flow generator according to claim 7, wherein a load capacity of the tapered roller on the side close to the blade is increased. 前記複列円錐ころ軸受は、左右の列の円錐ころの大径側端部を向かい合わせた正面組み合わせ軸受であって、
前記ブレードに遠い側の前記円錐ころの負荷容量を大きくしたことを特徴とする、請求項７に記載の風量発電機の主軸支持構造。 The double row tapered roller bearing is a front combination bearing in which the large diameter side ends of the tapered rollers in the left and right rows face each other,
The main shaft support structure for an air flow generator according to claim 7, wherein a load capacity of the tapered roller on a side far from the blade is increased.
JP2004371363A 2004-12-22 2004-12-22 Tapered roller bearing with aligning ring Withdrawn JP2006177446A (en)

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JP2008064244A (en) * 2006-09-08 2008-03-21 Ntn Corp Spindle supporting structure for wind power generator
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US8764304B2 (en) 2006-09-08 2014-07-01 Ntn Corporation Roller bearing, retainer segment of roller bearing for supporting main shaft of wind-power generator, and main shaft support structure of wind-power generator
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JP2008064244A (en) * 2006-09-08 2008-03-21 Ntn Corp Spindle supporting structure for wind power generator
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US8920040B2 (en) 2011-02-02 2014-12-30 Aktienbolaget Skf Rolling element bearing
DE102011003513A1 (en) * 2011-02-02 2012-08-02 Aktiebolaget Skf roller bearing
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CN110520641B (en) * 2017-03-31 2021-07-13 蒂森克虏伯罗特艾德德国有限公司 Rolling bearing device and wind turbine
CN107605940A (en) * 2017-10-24 2018-01-19 无锡民联汽车零部件有限公司 Double raceway tapered roller bearings
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